Compressor structure



March 19, 1963 3,081,931

F. ANDRASEVITZ COMPRESSOR STRUCTURE 2 Sheets-Sheet 1 Filed Oct. 30, 1961 INVENTOR. FRANK ANDRASEVIT Z wg c ATTORNEY March 19, 1963 F. ANDRASEVITZ COMPRESSOR STRUCTURE 2 Sheets-Sheet 2 Filed Oct. 50, 1961 INVENTOR. FRANK ANDRASEVITZ FIG. 6

BY mam ATTORNEY United States Patent 3,031,931 CGMPRESSUR STRUCTURE Frank Andrasevitz, San Pedro, Califi, assignor of fortynine percent to Manuel Saavedra and five percent to Juan I. Franko, San Pedro, Calif.

Filed Oct. 30, 1961, Ser. No. 148,556 7 Claims. (Cl. 230-44) The present invention relates generally to air or gas compressors, and more particularly to an improved form thereof. Although innumerable forms of gas and air compressors have been designed and used for a long period of time, most of these devices available heretofore have been of large, heavy construction and bulky. Due to their weight and the friction between the moving parts thereof, they have been relatively inefficient and require an excessive amount of power to operate.

A primary object in devising the present invention is to provide a novel compressor for gas or air, in which the compression of the gas is carried out in successive stages, and with the moving parts thereof being relatively light in weight, and easily replaceable in case of damage, whereby under normal conditions the compressor requires a minimum of maintenance attention.

Another object of the present invention is to provide a compressor for air or gas that is compact in structure which requires substantially less space than compressors of like capacity available heretofore.

A still further object of the invention is to provide a multi-stage air or gas compressor that is highly efficient in operation, and requires substantially less power to operate than compressors of like capacity which have previously been available.

Yet another object of the invention is to provide a compressor for air or gas that can be operatively associated with an axial flow turbine or like prime mover when the compressor and turbine are disposed end-to-end in a common tubular member.

These and other objects and advantages of the invention will become apparent from the following description of a preferred form thereof, and from the accompanying drawings illustrating that form in which:

FIGURE 1 is a longitudinal cross-sectional view of the compressor of the present invention, together with an axial flow turbine operatively associated therewith, with both the compressor and turbine being disposed within the confines of a common shell;

FIGURE 2 is a transverse cross-sectional view of the compressor taken on line 2-2 of FIGURE 1;

FIGURE 3 is a transverse cross-sectional view of the compressor taken on line 33 of FIGURE 1;

FIGURE 4 is a transverse cross-sectional view of the compressor taken on line 4-4 of FIGURE 1;

FIGURE 5 is a transverse crosssectional view of the compressor taken on line 5-5 of FIGURE 1;

FIGURE 6 is a transverse cross-sectional view of the compressor taken on line 6'6 of FIGURE 1;

FIGURE 7 is an enlarged view of a portion of FIG- URE 2; and p FIGURE 8 is an enlarged View of a portion of FIG- URE 3.

Referring now to FIGURE 1 of the drawings for the general arrangement of the invention, it will be seen to include an elongate tubular member A of substantial transverse oross section that has an upwardly and outwardly flared open end B. First, second, third and fourth transverse walls C, D, E and F respectively are positioned within the confines of the tubular member A and longitudinally spaced from one another.

The first and second walls C and D are preferably held in this longitudinal spaced relationship by a first cylindrical band It that extends therebetween and is bonded or fastened to the interior surface of tubular member A by conventional means (not shown). The third and fourth walls E and F are likewise held in a desired longitudinal spacing within the confines of member A by a second circular band 12 that extends therebetween and is also fastened to the interior surface of the member by conventional means. The means used in affixing the bands 16 and 12 to the interior surface of member A are prefer-ably of such form that the members 10 and 12 can be separated from the member A if necessary for maintenance reasons.

The first, second, and third walls C, D and E, respectively, have four sets of longitudinally aligned openings 14, 16 and 18, respectively, formed therein, which are spaced equidistant from one another, as may best be seen in FIGURE 5, whereby the sets of openings are spaced on centers. Each of the sets of openings '14, 16 and 18 serves to rotatably support a hollow driven shaft G (FIG- URE 1). Each of the shafts G has a first transverse plate 20 situated within the confines thereof and bonded to the interior of the shaft G by welding, or the like. Each plate 20 is so located in one of the shafts G as to be situated between the first and second walls C and D.

Three collars 22, 24 and 2d are mounted in fixed positions on each shaft G, and these collars abut against the exterior surfaces of the first, second and third walls C, D, and E, to maintain the shaft in a fixed longitudinal position relative to the tubular member A. The forward end of each of the shafts G is closed by a second plate 23, as may best be seen in FIGURE 1.

Four first tubular compressor members H are provided, as well as four second tubular compressor members I. The second compressor members I are substantially smaller in transverse cross section than the first compressor members H. Compressor members H and I are arranged in sets, with each member I being concentrically disposed within the confines of one member H, with the forwardly extending portion of one of the shafts G being concentrically situated within the interior of the second compressor J, as shown in FIGURE 1.

Each compressor member H is held in a desired radial spacing relative to one of the second compressor members I by two sets of sealed ball bearing assemblies 30 and 32 respectively. The outer races of the ball bearing assern blies 3i? and 32 are alfixed to the interior end sections of one of the first tubular compressor members H, and the inner races to the exterior end portions to one of the second tubular members I.

In FIGURE 1 it will be seen that the second tubular member I is somewhat longer than the first tubular member H. The outer and inner races of the ball bearing assemblies 3% and 32 are separated from one another in a conventional manner by a number of hardened steel balls K. Two sets of sealed ball bearing assemblies 34 and 36 are provided for each of the shafts G (FIGURE 1). The outer races of each of the ball bearing assemblies 34 is affixed to the forward interior surface of one of the second tubular compressor members I. The outer races of each of the ball bearing assemblies 36 is afiixed to the rear interior portion of one of the second tubular members I.

The inner races of the ball bearing assemblies 34 and 3d are affixed to the forward and rear exterior surface portions of the shafts G, as again may best be seen in FIGURE 1. These sets of ball bearing assemblies 30, 32 and 34-, 36 serve to hold the first and second tubular compressor members H and J, respectively, in a desired longitudinal relationship with the shaft G on which they are mounted, with the forward surfaces of the ball bearing assemblies 36* and 34 preferably being flush with the for- 3 ward ends 38 of the shaft G with which they are associated.

A cone-shaped cap 40 is provided for each of the shafts G and the rear edge surface of this cap is in abutting contact with the forward edge surface of one of the first tubular compressor members H. Cap 40 may be welded or otherwise affixed to the forward edge of the member H. Each tubular compressor member H has a first ring gear L mounted on the rear end thereof, and each compressor member I also has a second ring gear M mounted on the rear end thereof. A third ring gear N is provided for each of the shafts G which is mounted in a transverse encircling position thereon and rigidly affixed thereto, as shown in FIGURE 1.

Each set of first, second and third ring gears L, M and N respectively, engages driving gears O, P and Q. The driving gears O, P and Q are preferably formed as an integral unit and rigidly aifixed to a driving shaft R by means of a collar S. Collar S is held in a fixed nonrotatable position on a driving shaft R by a screw T, or other conventional fastening means. The driving shaft R is rotated by a prime mover (not shown) located forwardly of the upwardly and outwardly tapering portion B of the tubular shell A. Shaft R is rotatably supported in two aligned openings 42 and 44 formed in the first and second Walls C and D, respectively.

A boss 46 projects forwardly from the center of the third wall E and serves to house a ball bearing assembly 48. The outer race of assembly 48 engages the interior surface of boss 46, with the inner race of the assembly being rigidly affixed by conventional means to the rear exterior end of the driving shaft R. The inner and outer races of the ball bearing assembly 48 are, in the conventional manner, movably separated from one another by a number of hardened steel balls K. Although the shaft G and driving shaft R shown in FIGURE 1 are rotatably supported by the openings 14, 16 and 18, 42 and 44 respectively, it will be apparent that if desired, suitable anti-friction bearings such as ball bearing assemblies (not shown) may be disposed within the confines of these openings to rotatably support the shaft as well as the driving shaft R.

Each of the first tubular compressor members H has a longitudinally extending air inlet opening U formed therein through which air is forced by an air scoop 59 that is disposed adjacent thereto when the member H rotates. Each of the second tubular compressor members I has a longitudinally extending air inlet opening V formed therein through which air is forced by an air scoop 54 when the second member is rotated. Each of the shafts G between the ball bearing assemblies 34 and 36 has a longitudinally extending air inlet opening W formed therein that has an air scoop 58 associated therewith.

Each of the first tubular compressor members, together with one of the second members I and the ball bearing assemblies 36 and 32, cooperatively define a first enclosed space 62 into which air or gas may discharge through one of the openings U. Each of the second tubular compressor members J, together with the shaft G on which it is mounted, as well as one of the sets of ball bearing assemblies 34 and 36, cooperatively define a second enclosed space 64 into which air or gas can discharge through one of the openings V, as best shown in FIGURE 5. The plates 26 and 28 in each of the shafts G cooperatively define a first elongate confined space 66 into which gas or air can be discharged through opening W.

When the shaft R is driven in a clockwise direction, as shown in FIGURE 5, the gears O, P and Q are concurrently rotated. The gears O, P and Q are driving gears and concurrently cause rotation of the four sets of ring gears L, M and N. As the sets of rings gears L, M and N are rotated, the first and second compressor members H and I respectively, are rotated, as are the shafts G. As each of the first tubular compressor members H rotates, air from the ambient atmosphere is forced into the confines of the confined space 62, and this entry of additional air from the ambient atmosphere into space 62 increases the air pressure therein to a first increased pressure X. Air under pressure X in each of the confined spaces 62 is, of course, subjected to the action of one of the rotating second tubular compressor members I. The air scoops 54 on members I cause air at pressure X to be scooped up during rotation of members I to force air therein and raise the air pressure in the enclosed spaces 64 to a second increased pressure X1.

The air at pressure X1 in each space 64 is then subjected to the action of one of the rotating shafts G where by the air scoops 58 thereon force the air into confined spaces 66 to raise the air pressure therein to a third increased pressure X-Z. The confined space 66 in each shaft G is defined by the interior surface of the shaft and the interior surfaces of the plates 20 and 28.

The interior surfaces of the first and second walls C and D, and the interior surface of ring 10, serve to define a first compartment 68. An angular U-shaped slit is made in each shaft G within the confines of one of the compartments 68, with the portion of the shaft within the boundaries of the slit being bent outwardly, as shown in FIGURE 7, to define an air discharge opening 70 and an outwardly extending lip 72. Air at the third increased pressure X-2 in first confined space 66 discharges therefrom into the compartment 68.

Each of the shafts G on the right-hand side of plate 20, but still within the confines of the compartment 68, has an angular U-shaped slit formed therein, with the material within the confines of the slit being bent out- Wardly as shown in FIGURE 8 to define an air scoop 76. This also results in formation of an air inlet opening 74 in each of the shafts G. As the scoops 76 rotate in compartment 68 they force air at third pressure X-2 therein into inlet openings 74. Upon entering one of the inlet openings 74 at the third pressure X-2, the air pressure in a confined space 76 defined on the right of plate 20 increases to a fourth pressure X3. The right-hand ends of shafts G (FIGURE 1) are closed by plates 78. Thus it will be seen that the spaces 76 are defined by the plates 20 and '78 and the interior surfaces of shafts G to the right of the plates 20.

Portions of the shafts G project into a second compartment 80 defined by the third and fourth walls E and F and the ring 12. The portions of shafts G situated in second compartment 80 have angular U-shaped slits formed therein. The material within the confines of these slits is deformed outwardly as shown in FIGURE 6 to form air discharge openings 82 and lips 84. Air at pressure X-3 discharges from the openings 82 into the second compartment 80. Air at the fourth increased pressure X3 can discharge from the second compartment 80 through a flow regulating valve 86 that is in communication with a rearwardly extending passage formed in fourth wall F.

A tubular housing 88 of an axial fiow turbine 90 is disposed in coaxial alignment with the rear portion of tubular member A and affixed thereto by conventional means, such as welding or the like. A centrally disposed body 92 is provided that defines a rearwardly extending boss 4 in which a ball bearing assembly 96 is mounted. A number of rigid legs 98 extend outwardly from body 92 and are affixed to the forward end of housing 88. The ball bearing assembly 96 rotatably supports a shaft 99 that is connected to the forward end of a rotor'100. A driving shaft 102 extends rearwardly from rotor 100, and may be used to power such equipment (not shown) that is to be driven by the turbine 20. The air initially at the fourth increased pressure X-3, after flowing through valve 86 and turbine 90, discharges to the ambient atmosphere.

The operation of the invention has been explained hereinabove, but may be summarized as follows. As the shaft R is driven, the four sets of first and second tubular compressor members H and J are rotated, as are the shafts G. Rotation of these members and the shafts G cause air to be drawn rearwardly in tubular member A, the pressure thereof is increased to pressure X-3 when it discharged into the second compartment 80. At the increased pressure X3, the air then flows through valve 86 at a desired rate to actuate the axial flow turbine 90. If desired, the axial flow turbine may be eliminated and the air at pressure X3 used as it discharges from passage 88 for any desired purpose.

Although the present invention is fully capable of achieving the objects and providing the advantages hereinbefore mentioned, it is to be understood that it is merely illustrative of the presently preferred embodiments thereof and I do not mean to be limited to the details of construction herein shown and described other than as defined in the appended claims.

I claim:

1. An air compressor structure comprising:

(a) an elongate tubular shell having an open forward end;

(b) A plurality of sets of first and second tubular compressor members longitudinally disposed on the forward portion of said shell and circumferentially spaced from one another, with said second compressor member in each of said sets being disposed in one of said first compressor members and radially spaced therefrom, each of which first and second compressor members have an air inlet opening formed therewith with a first air scoop operatively associated with said opening;

(c) a plurality of longitudinally extending hollow first shafts disposed in said tubular shell that have said sets of first and second compressor members concentrically disposed on the forward end ortions thereof, said shafts having air inlet openings formed in said forward end portions with second air scoops associated with said openings in said shafts;

(d) a plurality of sets of sealed ball bearing assemblies at the forward and rear ends of said first and second tubular members for rotatably supporting said first members on said second members and said second members on said forward end portions of said first shafts;

(e) a plurality of transverse longitudinally spaced walls in said tubular shell defining first and second compartments therein, said walls having a plurality of sets of longitudinally aligned openings formed therein in which said first shafts are rotatably supported,

with the portion of each of said shafts in said firstcompartment having first air discharge openings formed therein and second air inlet openings with third air scoops operatively associated therewith, with the portions of said shafts in said second compartments having second air discharge openings formed therein;

(7) a plurality of first plates transversely disposed in said first shafts between said first =air discharge opening and said second air inlet openings;

(g) a plurality of second and third plates afiixed to 6 the forward and rear end of said first shafts, which first, second and third plates cooperatively define first forward confined spaces and second rear confined spaces in said first shafts;

(h) a longitudinally extending driving shaft disposed in said tubular shell;

(1') first means on said driving shaft for concurrently rotating said first shafts and said first and second tubular compressor members, with air as said first plurality of said sets of first and second compressor members and first shafts are rotated being forced from the ambient atmosphere into said first compressor members by said first scoops thereon to increase the pressure of air in said first compressor members to an increased first pressure, with said second rotating compressor members forcing said air at said first increased pressure into the interior thereof to have a second increased pressure, said rotating first shafts forcing said air at said second increased pressure into said first confined spaces to have a third increased pressure, said air at said increased third pressure discharging into said first compartments, said air at said third increased pressure being forced into said second confined spaces by said rotating third air scoops on said first shafts to have a fourth increased pressure;

(j) and passage means in the rearwardmost of said Walls through which said air at said fourth pressure can flow rearwardly relative to said tubular shell.

2. An air compressor as defined in claim 1 wherein said first means comprise a plurality of circular members which are drivingly associated with a plurality of circular members affixed to said first and second compressor members and said driven shaft.

3. An air compressor as defined in claim 1 wherein said first means comprise a plurality of gears on said driving shaft that engage a plurality of gears rigidly mounted on said first and second compressor members and said driven shafts.

4. An air compressor as defined in claim 1 which also includes a valve for controlling the rate at which said air at said fourth pressure discharges rearwardly through said passage means.

5. An air compressor as defined in claim 1 which also includes means on said driven shafts for maintaining said driven shafts in fixed longitudinal relationship with said driving shaft.

6. An air compressor as defined in claim 1 which also includes an axial fiow turbine directly connected to the rear portion of said tubular shell, with said turbine being driven by said air at said fourth pressure.

7. An air compressor as defined in claim 3 which also includes a second ball bearing assembly that rotatably supports the rear end of said driving shaft;

([1) and means for supporting said second ball bearing assembly from the forward face of the rearwardmost of said walls.

No references cited. 

1. AN AIR COMPRESSOR STRUCTURE COMPRISING: (A) AN ELONGATE TUBULAR SHELL HAVING AN OPEN FORWARD END; (B) A PLURALITY OF SETS OF FIRST AND SECOND TUBULAR COMPRESSOR MEMBERS LONGITUDINALLY DISPOSED ON THE FORWARD PORTION OF SAID SHELL AND CIRCUMFERENTIALLY SPACED FROM ONE ANOTHER, WITH SAID SECOND COMPRESSOR MEMBER IN EACH OF SAID SETS BEING DISPOSED IN ONE OF SAID FIRST COMPRESSOR MEMBERS AND RADIALLY SPACED THEREFROM, EACH OF WHICH FIRST AND SECOND COMPRESSOR MEMBERS HAVE AN AIR INLET OPENING FORMED THEREWITH WITH A FIRST AIR SCOOP OPERATIVELY ASSOCIATED WITH SAID OPENING; (C) A PLURALITY OF LONGITUDINALLY EXTENDING HOLLOW FIRST SHAFTS DISPOSED IN SAID TUBULAR SHELL THAT HAVE SAID SETS OF FIRST AND SECOND COMPRESSOR MEMBERS CONCENTRICALLY DISPOSED ON THE FORWARD END PORTIONS THEREOF, SAID SHAFTS HAVING AIR INLET OPENINGS FORMED IN SAID FORWARD END PORTIONS WITH SECOND AIR SCOOPS ASSOCIATED WITH SAID OPENINGS IN SAID SHAFTS; (D) A PLURALITY OF SETS OF SEALED BALL BEARING ASSEMBLIES AT THE FORWARD AND REAR ENDS OF SAID FIRST AND SECOND TUBULAR MEMBERS FOR ROTATABLY SUPPORTING SAID FIRST MEMBERS ON SAID SECOND MEMBERS AND SAID SECOND MEMBERS ON SAID FORWARD END PORTIONS OF SAID FIRST SHAFTS; (E) A PLURALITY OF TRANSVERSE LONGITUDINALLY SPACED WALLS IN SAID TUBULAR SHELL DEFINING FIRST AND SECOND COMPARTMENTS THEREIN, SAID WALLS HAVING A PLURALITY OF SETS OF LONGITUDINALLY ALIGNED OPENINGS FORMED THEREIN IN WHICH SAID FIRST SHAFTS ARE ROTATABLY SUPPORTED, WITH THE PORTION OF EACH OF SAID SHAFTS IN SAID FIRST COMPARTMENT HAVING FIRST AIR DISCHARGE OPENINGS FORMED THEREIN AND SECOND AIR INLET OPENINGS WITH THIRD AIR SCOOPS OPERATIVELY ASSOCIATED THEREWITH, WITH THE PORTIONS OF SAID SHAFTS IN SAID SECOND COMPARTMENTS HAVING SECOND AIR DISCHARGE OPENINGS FORMED THEREIN; (F) A PLURALITY OF FIRST PLATES TRANSVERSELY DISPOSED IN SAID FIRST SHAFTS BETWEEN SAID FIRST AIR DISCHARGE OPENING AND SAID SECOND AIR INLET OPENINGS; (G) A PLURALITY OF SECOND AND THIRD PLATES AFFIXED TO THE FORWARD AND REAR END OF SAID FIRST SHAFTS, WHICH FIRST, SECOND AND THIRD PLATES COOPERATIVELY DEFINE FIRST FORWARD CONFINED SPACES AND SECOND REAR CONFINED SPACES IN SAID FIRST SHAFTS; (H) A LONGITUDINALLY EXTENDING DRIVING SHAFT DISPOSED IN SAID TUBULAR SHELL; (I) FIRST MEANS ON SAID DRIVING SHAFT FOR CONCURRENTLY ROTATING SAID FIRST SHAFTS AND SAID FIRST AND SECOND TUBULAR COMPRESSOR MEMBERS, WITH AIR AS SAID FIRST PLURALITY OF SAID SETS OF FIRST AND SECOND COMPRESSOR MEMBERS AND FIRST SHAFTS ARE ROTATED BEING FORCED FROM THE AMBIENT ATMOSPHERE INTO SAID FIRST COMPRESSOR MEMBERS BY SAID FIRST SCOOPS THEREON TO INCREASE THE PRESSURE OF AIR IN SAID FIRST COMPRESSOR MEMBERS TO AN INCREASED FIRST PRESSURE, WITH SAID SECOND ROTATING COMPRESSOR MEMBERS FORCING SAID AIR AT SAID FIRST INCREASED PRESSURE INTO THE INTERIOR THEREOF TO HAVE A SECOND INCREASED PRESSURE, SAID ROTATING FIRST SHAFTS FORCING SAID AIR AT SAID SECOND INCREASED PRESSURE INTO SAID FIRST CONFINED SPACES TO HAVE A THIRD INCREASED PRESSURE, SAID AIR AT SAID INCREASED THIRD PRESSURE DISCHARGING INTO SAID FIRST COMPARTMENTS, SAID AIR AT SAID THIRD INCREASED PRESSURE BEING FORCED INTO SAID SECOND CONFINED SPACES BY SAID ROTATING THIRD AIR SCOOPS ON SAID FIRST SHAFTS TO HAVE A FOURTH INCREASED PRESSURE; (J) AND PASSAGE MEANS IN THE REARWARDMOST OF SAID WALLS THROUGH WHICH SAID AIR AT SAID FOURTH PRESSURE CAN FLOW REARWARDLY RELATIVE TO SAID TUBULAR SHELL. 